Transmission



May 27, 1952 R. T. BURNETT TRANSMISSION Filed July 3o,-` 1948 5 Sheets-Sheet l May 27, 1952 R. T. BURNETT TRANSMISSION 3 Sheets-Sheet 2.

Filed July 30, 1948 Mnh MVN

R. T. BURNETT TRANSMISSION May 27, 1952 s sheets-sheet s Filed July 30, 1948 REN.

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ATTORNEY Patented May 27, 1952 2,598,501 .'rnANsMIssioN;

Richard T. Burnttg South-Bend; Indi; assigner-to-` Be'dix Aviation Corporation; 1 S o1ith.JBen'd,'.Ind:, acorporatiomof.Delaware;

1 lThis vinvention relates to transmissions embodying hydroekinetic torque converters- An important object of the invention is toj pro- Vide a hydro-kinetic transmission in which the reaction wheel is rotated forward during torque-` multiplication. to thereby obtain rising engine speedwithincreasing speed ratio when .used with an internal-combustion engine. n

Another importantkobje'ct of' the invention resides in the provision ofa transmissionequipped with a hydro-kinetic torque converter having; rotatable bladed turbine andi reaction ywheelszinteroonnected through aplanetary gear train in such a manner that the'turbine Wheeltdrives the reaction wheel forward at: times of torque-'multiplication.

A still. further important object ofthe invention resides in the provision of," a transmission embodying a hydro-kinetic torque converterinterconnected'with aA single planetary gear,L train in such a manner as to provide forwardland reverse drive.

An object of'the invention resides inftlie vprovision ofY a transmission having continuous Variable speed and torque Without shifts orinterruptions o rvsudden change of input'speed.'v

A yet' further object: ofgthe inventioniisto provide au'id pumplfor a hydrokinetictransmisf .sion,vw1iicl1 pmnp maybe connected, either di-V rectlyv to the, input shaft to .be engine driven. or to the output through a planetary gear train whena vehicle .in Whichthe transmission is ,i n corporated is being pushed Yor towedfor, starting.

The aboveanciother objects and features of the invention vwill be apparent from the-following description of theapparatus taken inconnection with the accompanying drawingsivhich form a partof this speciiication, andin which:

Figure -1- isa: longitudinai sectional 'View' of the trans'I 'n'is'sionl of nthe invention; `withY parts in elevation: t l r .Y

Figure 2- isja: longitudinalsectional View of a mourned-formertransmission; Withpart's in eleration: :and-'- t, o Y t,

Figure show'sthe performance-*curves of the transmission of Figure l.

Referring.l noW--to -Figure 1 for a Vdetailed description of v-the-tra-nsmissi'on-of my inventionjthe reference numeral i I 0 designates a housinglvvhlch.

may be'- suitably securd--tog-an automobile kengin.- not shown. Energy fromtheengine is transferred to an input shaft or; crankshaft' vl2, is driva-bl-y connected" toi ahydro-'Iliinetic torque'c'crnverter44.I

Thetorque converter-comprises' an irripel'lerI "1- centric-*sleeves orf shafts 3B@ and` 38 respectively.

The turbine and reaction` lvv-heelsg 28T andl 31u21 are provided with hubs 40 andf-Zlres'pectively; which tover -saidone end of sleeve i361; The hubs-.are carried on the -sleeve 3 6 between l the hollow ystub shaft-members 32 and 345- Hub 40,' of' the turbine-Wheel, its rotatably supported on a sleeve bearing 415,L interposed between the hub' fand-said sleeve: Hub 42, of thereaction wheel, is-securly `finedto sleeveV 36. The impellen turbine,

-and-reaotion-Wheels are so shaped that together they provideafclosed hydraulic circuit or toroidal channel 46g throughl which Ailuid .is circulated by pellerblades-orvanes 48 Amounted 'in acircular-row--on the impeller Wheel-.T Th-ismovingflu'id,

- 'setir 'motionbythe imp'eiierblades; actson blades-or vanes- S'ldisposed in a circular rovi-.on the-turbine-Wheel; to-thereby impart rotation-to the turbine wheel. The reaction Wheel 30 is equippedy with a circularrow of blades or varies are-constitutedto take reaction from the' moving fluid asv well-as control the direction ofowofi the uid at' the entrance-of thefiinpeller-Whee'l, to thereby-multiply-torque into'lthe turbine wheelsV The-f construction and-arrangement-ofItlieXva-nes are suchA as to producean overdriving eiectonV the turbine Wheel,l asfdescribe'dLin-.my application entitled Torque Con vetten" serialiNo; 701,595, led .;Oct"oben:5;'f1946. Althoughtheft/orque converter of. the instantapplication-:utilizes 'the same princi-ples-ffor'obtaining foverdrive; as my, previously,v menti'uned .'led application, ythe;design and-arrangements@the impeller and turbine vanes ofv Vlthe l ierein V disclosed converterrdiifer-overthe,earlier-filed applicat iQn. l Aj torquemintipiyingE planetary gear traint; is interposed between the ,torque.conveifter i l and output shaft, 54, ,to the outer end' ofwhioli vis splined, ayokeL 6... The ygear traicompris'es'ga planetv carrier 58;' revolvably mountedon sleeve bearings 60. A free wheel device 62 is interposed between the planet carrier 58 and a brake band 64 to allow free rotation of said planet carrier in one direction beyond a one-to-one torque ratio of the transmission ibut to hold said planet carrier from rotation in the other direction during torque multiplication. This, of course, is based on the assumption that the brake band 64 which conditions the transmission for forward drive, is frictionally engaged with external wheel 66 of the free Wheel device. With the brake band 64 out of Contact with the wheel 66, the planet carrier is free to rotate in either direction. Any suitable means may be employed to operate the brake band 64, such for example, as hydraulic actuation, not shown. Axially extending pins 68 are carried by the planet carrier 58, for rotatably supporting a cluster of planet pinions 10, 12, and 14. These pinions 10, 12, and 14 are integrally related. A drum 16 is splined to one end of the sleeve 38, to the other end of which is fixedly attached the turbine wheel 28. A brake band 18, which connects the transmission for reverse, is arranged for frictional engagement with the drum 16. Any suitable means may be employed for actuating the brake band 18, such, for example, as hydraulic actuation, not shown. Frictional engagement of drum 16, holds the turbine wheel stationary for a purpose to be hereinafter described. A sun gear 80 is carried on the drum 16 for meshing engagement with the pinions 10. The hollow sleeve 36, which carries the reaction wheel 30, is provided with a sun gear 82 arranged for driving engagement with the planet pinions 12. The inner end of driven shaft 54 is equipped with a sun gear 84 which engages the teeth of planet pinion 14.

In the planetary gearing arrangement of Figure 1, the gear ratios are such that with the planet carrier 58 held xed to accomplish forward drive the torque transmitted to the output shaft 54 from the turbine shaft 38 is approximately 1.5 (one and a half) times the torque impressed on the turbine shaft 38 up to the clutch point of the transmission, at which time input torque equals output torque. During this same period prior to the clutch point of the transmission, that is, prior to one to one torque ratio, the negative torque transmitted to the output shaft 54 from the guide shaft 36 is approximately only .'7 (seven tenths) times the torque impressed on the reaction or guide shaft 36.

When in reverse drive the clutch band 18 locks sun gear 80, which is integrally related to shaft 38, to the other end of which is fixed the turbine wheel 50, The reaction wheel, which is nowfree to rotate, is driven in a direction opposite to the impeller Wheel to thereby drive sun gear 82 which meshes with the planet pinions 12. Since the planet carrier is now free to rotate, the planet pinions 12 rotate about pins 68 as a moving center, driving the output shaft 54, through gears 14 and 84, with the reaction being taken through gears and 80 into the band 13. In the present illustration the gear ratio of the guide shaft 36 to the output shaft 54 is in the neighborhood of 1.7 to 1. This ratio obviously provides for a relatively high torque at the output shaft compared to the torque impressed on the guide or reaction shaft at any instant of time. It is to be understood that wherever speciiic values are used herein it is for purpose of illustration only and the specification is therefore not to be limited thereby.

In order to pressurize the fluid for actuating the bands 64 and 18 and to put the fluid in the toroidal channel 46 under pressure a pump 9| is provided. The pump herein used to put the fluid under pressure is believed to embrace certain novel two-way driving features hereinafter described. The housing I0 is formed with an internal radially extending flange 86, drilled and threaded axially at 88 for the reception of screws S0, one only of which is shown. The screws pass through a pump housing S2 and threadedly engage the radial flange. A pump rotor 94 is mounted on a sleeve 96 to be driven thereby through a ball member 08. The sleeve 86 is concentrically positioned with respect to the sleeve 38 and rotates on sleeve bearings |00 interposed between the sleeve 38 and the sleeve 96. The latter sleeve is driven by two one-way clutches |02 and |84 but at different times, depending on which is rotating faster, the turbine or impeller wheel. The one-way clutch |02 is drivably interposed between the hollow stub shaft member 34 and the sleeve 96 so that when the speed ratio of turbine wheel to impeller wheel is less than one to one the pump rotor 94 will be revolved by the impeller to thereby pressurize the hydraulic circuit. Beyond a one to one speed ratio of turbine to impeller wheel the turbine wheel speed will be greater and hence drive the pump rotor. A collar member |06 connects the member 34 to the one-way clutch |02. When the speed ratio of turbine to impeller is less than one to one the one-way clutch |04, which is drivably interposed between the sleeve 96 and the sleeve 38. is overrunning. However, when the speed ratio of turbine to impeller is greater than one to one, as would be the case some time before the clutch point of the transmission was reached, as indicated by the intersection of the curves at 0, the turbine wheel, which is integral with sleeve 38, drives the pump rotor 94. At this time, the one-way clutch |02 is overrunning. A collar member |08 drivably connects the sleeve 38 to the one-way clutch |04. Outlet ||0 of the pump communicates with the toroidal channel 46 through passages H2, |I4, and H6. The toroidal channel 46 communicates with reservoir H8 through passages |20, |22, |24, past valve |26 and hence back to the reservoir via a conduit, not shown. The inlet of the pump, not shown, Communicates with the reservoir l |8, through an internal passage, not shown. The pump per se forms no part of the present invention but, as aforementioned, the manner of driving the same from two sources is believed novel.

A one-way clutch |30 is interposed between the concentric shaft 36 and the input shaft i2 so that this shaft can be driven by the vehicle at times to thereby drive the engine, not shown, so as to produce a braking or decelerating action on said vehicle. This mechanism is claimed per se in my application Serial No. 5,546, :tiled January 31, '1948.

With reference to Figure 3 torque is represented by full line curves and R. P. M. by broken line curves. The reaction in the transmission is represented as a negative torque below the abscissa. The reaction on the guide or reaction wheel will be negative so long as the torque converter multiplies torque. As soon as torque multiplication in the converter has ceased, that 1s, torque input to the converter equals torque .output .oi-the contenter. .the .reaetion torque hef :comestzero as. indicated; by. Ythe intersection .of the` absoissa .and th. TgeQtQIi iii-@mue Finnois commonly. iermedf-.thecluton D 0f converter and that: pointU at. Wh n. Ithe nuidientersfthe .guide .or reaction vwheel. vat, such an. angle that; noehengefin angular. .momentum .Qfthe nuidrtakesplaoe. A:verticaliline C-has heen. drawn. through, this'. point-.for ready. reference to the oorldition-.oithe .elements of the transmission. Although thefreaotion torque 0f the reaction wheel .hagbecoine Zero.. `as aforementioned., the. total reaction. tanque .of- 'V the .transmis/sterile,stiilfznegative .due to .torduemule .tiplioation in.. the planetary gear. train. .5.23 .as hestf Shown. in Figure f3 :where the .totalreaction .torqueisibelowcthe abscissa. Whentoroue mul.-

.tinlication of: `the transmissi0nl ceases.. that..

zinnutsandzoutput; .torduebecomeequa-l, the total reaction torque. .becomes zero. asindioatediby 'theinterseetiom offthe. total;. .reaction toroue.

curye. withtheahscissa. Tjhis. point. of .intersection-oi the total reaction.torquefteurve with the. absoissa .is defined. as. the clutch point. of

thetransmission andv a vertical line isdrawn therethrough for ready reference toftheoondition ofother elements ofA the ktransrn-ission at this-noint..

With. the. output shaftsneed; curve .as arefer eneeitgwill henotedthatthe reactionwheel speed increases at a slower rate and the turbine. Wheel spendi-increases. at; agreater Vrateup .to the, clutch point of the.. transmission. rbeyond. which .the curves representing'. the.. reaction and turbine wheel speeds converge on the curve representing.. vthe output.- shait speed.

From astall conditionwith theengine idling riSeSitQ'gZO P: at. the clutch point T; of the transmission, during. which time engine .torque` has. remained. substantially constant as showngby the enginetorque curve. The output .shaft andfenginespeed curvestend to converge .attheclutch looint; .Beyondatheclutchpoint T, thatis,v during thecoupling range, engine; speed .continuesto be greater thanoutput shaftfspeed with,.a`relaltivel-y.small percentage ofslip .between Between stall; andgthe clutch. point C of the converter the, output torque at any instant is .equalv to thetotalzturhine torque in. theplanetary gear train which isrepresentedzby, curve 1.428 turbine torque, minus. .5.giuideV torque. Beyond thm clutch. points G oi; .the .converterathognide Wheel; .torque becomes.. positiveand= isaddedf to i.

.con-nected.. to a torque. converter: 21.4; similar; in

oonstruction to that: of Figure la, and-:haring an inineller. wheell 21.6, turbine...-Whee l228,f and'. iride or. reaction Wheel; 2x30; Concentrieally related shafgtsfl.; and 2-38; aredrivably. conneetediat one .endf tof-the.. reaction wheel. 23.8.1: and turbine wheel 228:.- resnectively. Totheother.- ends: of shaiftsflyand. 2 8i. areysnlined--a-snn gea-r .2.82, and aringogearf-2-1..respectively, Comprisingitno geen elements. .of-1. a-..nia-netary. geartrain 2.5.2.

terposed `between,.the.turbineian@reaction=wheels on` the one liand,.and kbetween .these Awheels and output shaft 25,11 on `the other.4 hand; planet carrier 2.5.8; is ,integral with `one end of the output .shaft 254; anais. provided with. .a nin 2618i on whichpinions 2];I-.and213 are. mountedrformesh- 'ing engagement :with sunv gear 2.82. and iii-ng gear l28dz.res uectively. Asecond sun gear-283.engages the .teeth of.A the pinion. 2l3andgis;integ1jal with a sleeve shaftv 28:5. concentrioally;:nosinonedfwith respect to the output .shagft 2.51%aridA carried by an. axially extending -wall 28S! .of housing ,21.0. A free wheel device-.252 is interposed between the second sun. gear 28.3;l and a forwardf drive brake band 254.to .allowireeiotation of s .dsecond sun gear. in.. one.; direction beyond; torque unityl in the transmission but to hold said second -su-n gear from rotation in the other direction during torque multiplication. Any suitable means, such as` hydraulic actuation, .notshown may. .be vemployed .to actuate brake ,band .264:.to cause the same to frictionally .engage .external wheel. 2&5: of vthe freewheel. device. When-.tbnake band 2&4. vis.` out .offcontact with. wheelrzi the second. sun gearisfree. to rotatefin either.. direction. Brake bandii; :which .mayabeiactuated-:iu a.- manner` similar-- to. brake handxfz', is. .consti-'- tutedpto irictonally engagesunport '2i-.Giv which carresithe. ring. gear. 28.1,', to. thereby. holo the turbnewheel and :hence the ring ygear stationary when. the. transmission.. is connectedi forfreuerse drive. During. thistime the. orwardzhralcc hand .2:64 is released.. When. .connected-.im .thisrmanr neig the. guide wheeli-isrotatedsinf.a direotion;.onposite to that of the impeller. wheelzso .as-taime partfreverse. rotation to .thev output shaits; at which time the, sun-gear .2 82 driuesgthie .planet v carrier in areJ/ersedirection andante.- reduced speed:

Inforward drive, at which time/braheha-nd 25.118 isireleased :and brake bandt2z4i-engages-=whee1 213,6.; to. thereby.v hold .theA -second-r. sun Agean--283 against, ,rotation in... one direction, the;V turbine Wheel rotates.. in the.l saine. direction as the im.- nel1er-Wl'1eel, and-fthe ring: gear 28.| rotation-.the pinionsi. 2511i .andz 2:13, hence driving. the .planet carrier. forti-arci and turning .theiguide wheclzrin thesame vdirection asi-,the turbine;. 'wheel1fandxata-a xed-:speediratio Ereouently passing another; wehiele or to .ohtain.greaterptorque .atilow speeds, it is .defsirable to shiftdown.intonay lower gearito .obtain `additional torque; for. quiete acoelerat'on.4 and.. to thiseendi I have .provided wat. reduction gear .train 289i. whichis interposed::between` output shafts 254;and552515. This planetarygear train.. 28em= braces turing gear Zinsplined on theiopposi'te endzof aoutputs shaft. .2 de 'from the.. planeticarri'er 25.8.: Intermeshing with the ring `gearZtltni'sa pinion. 2.8i', pivotallyx mounted ona. pin 292, which. is. integral. with a planet. .carrierv 23u-securely xed to theinner end of output shatt255, .sQaasstQ rotate. said shaft. Aisun vgear 2931i's:`xed secured.; tothe. inner wall 29A\.of' an annular shapectsdnum.: Q5, rotatably mounted' onthe-axiallfy;:extendingv tubular portion- 29$1Lofthe-lions ing 2d'fz The; drum-.295mg alsoequippedfwim., an outer; Walk-2951i engageabfle .by a brake Vr' a-ndl2-9`8 when; i `seolesir-.edY toeholssaidsungearI 2153==2xed= Actua? nf'fsaid'brakebandSS-may he ypel'- formed 'i any-g suitablemannerg. such as hydraulic actuation; Ilot shown.. Aidisc-cli-l-tchvtis interposed? etmeen theidrumf. Ztrlanrd planet-"carrien 23;9;,. The .dises-.are .arrangedax-ially iny said drum and are supported alternately by the drum and planet carrier so that axial compression of said discs will tie the drum to the planet carrier to thereby rotate said drum and carrier as a unit. A fluid pressure operated piston 300 is disposed between the inner and outer walls 29A and 291 of the drum for axial displacement against said discs. A spring 3M normally urges said piston in a direction to relieve compression of the discs, as shown in the drawings, so that the planet carrier 239 is free to revolve, with respect to the sun gear 293. Fluid under pressure from a source, not'shown, is connected to a passage 382 which communicates with the back side of piston 300.

When the transmission is connected for direct drive, that is, with output shafts 254 and 255 rotating as a single shaft, brake band 298 is disengaged from the outer wall 291 and piston 300 is urged to the left under the influence of fluid under pressure, to thereby compress the disc clutch which couples the planet carrier and drum together as a unit.

Should it be desired to shift the transmission into a lower gear ratio to obtain additional torque for increasing vehicle acceleration the fluid under'pressure acting on the piston is released and the clutch band 298 is caused to engage the drum 295. The spring 301 will return the piston to the position shown in the drawing, which relieves the compression on the discs. gear 293 is now the fixed member of the planetary gear train and takes the reaction from the pinions of the planet carrier which now drives the output shaft 255 at a reduced speed with respect to output shaft 254.

Operation and function of the transmission:

Referring now to Figure 1, with the crankshaft l2 rotating and clutch bands 64 and 18 released, there can be no torque reaction and consequently no torque multiplication. If the forward brake band 64 is now caused to frictionally engage the external wheel 66 a negative torque reaction is taken thereby through the planet carrier 58, thence through the free wheel device 62. Shortly after the brake band has locked the transmission into forward drive, torque will be impressed on the output shaft 54, which will begin to rotate when the torque reaches a value sullicient to overcome the load on the output shaft. The torque impressed on the input shaft is first multiplied in the torque converter, thence transmitted through the sleeve 38, to which sun gear 80 is drivably connected, and into the planetary gear train 53, where the torque is again multiplied before being transferred to the output shaft. During the period of torque multiplication in the transmission, that is, as long. as torque output exceeds torque input, the reaction will be in a direction through said free wheel device 52 to lock the same against rotation. During this period the reaction wheel is driven forward in the same direction as the impeller and turbine wheels but at a rate less than turbine wheel speed. That is the reaction wheel is driven forward at a fixed ratio with respect to the turbine wheel. As hereinbefore explained this is accomplished by interposing the planetary gear train between the turbine and reaction wheels. Beyond a torque ratio of unity, that is, the clutch point of the transmission, at which time torque reaction in the transmission has ceased, the planet carrier 58 will be free to rotate in a direction opposite to that in which reaction was tending to rotate said planet carrier.

The sun At this time the torque converter is performing as a hydraulic coupling. As is obvious from an examination of the curves of Figure 3, beyond the clutch point of the transmission the turbine wheel speed rises at a slower rate, the engine speed rises at a greater rate, and tlie guide or reaction wheel speed also rises at an increased rate. This trend will continue with the input shaft speed approaching the output shaft speed as the car speed is increased.

Assume a condition in the transmission wherein the forward brake band 64 is released and the reverse brake band 18 is caused to frictionally engage the drum 16, to thereby lock the sun gear 80 against rotation. With this arrangement the turbine wheel 50 is held against rotation, since it is carried by the sleeve 38 onto which the locked sun gear 80 is splined. The reaction wheel will be revolved in a direction opposite to the impeller wheel, under the influence of the circulating fluid, to thereby drive the concentric shaft 36. The sun gear 82 is securely xed to the other end of the shaft 36 for driving engagement with the planet pinion 12. This drives the output shaft in a reverse direction and at a reduced speed.

Although this invention has been described in connection with certain specific embodiments, the principles are susceptible of numerous other applications that will readily occur to persons skilled in the art.

Having thus described the various features of the invention, what I claim as new and desire to secure by Letters Patent is:

I claim:

1. A transmission comprising a hydro-kinetic torque converter having rotatable bladed impeller, turbine, and reaction wheels, when rotated, said impeller wheel circulates fluid which acts on said turbine and reaction wheels tending to rotate the turbine wheel forward and the reaction wheel backward with respect to the impeller wheel, a planetary gear train including a planet carrier supporting a double planet pinion, a first gear element arranged in meshing relationship to one of said pinions, a connection between said first gear element and said turbine wheel, a second gear element arranged in meshing relationship to the other of said pinions, a connection between said second gear element and said reaction wheel, and means for taking reaction comprising a third gear element arranged in meshing relationship with said one pinion.

2. A transmission comprising a torque converter equipped with rotatable bladed impeller. turbine, and reaction wheels, when rotated, said impeller wheel circulates fluid which acts on said turbine and reaction wheels tending to drive the former forward and the latter in reverse with respect to the impeller wheel, a first gear connected to said turbine wheel, a second gear connected to said reaction wheel, a double planet pinion having different pitch diameters, one of said pinions meshing with said rst gear and the other meshing with said second gear to provide a positive forward drive to said reaction wheel, a planet carrier supporting said double planet pinion, an output shaft to which said planet carrier is connected, means for taking reaction when the output shaft is to be driven forward, and means for holding said first gear when the output shaft is to be driven in reverse. f

3. A transmission comprising a hydro-kinetic torque converter having rotatable bladed impeller, turbine, and reaction wheels, when ro- ,9 tated*I said impeller wheel circulates fluidwhich acts -onv said turbine and reaction wheels' tending to rotate the turbine Wheel vforward and `thereaction wheel backward with respect to the ifmpeller wheel, y-a planetary gear ftrain comprising a'rilane'tV carrier supportin'ga pair of planet' pinionslrelatively fixed-for rotation about a common axis. a gear' elementv arrangedv meshing relatioiship' with oneY of said pinions-.and having 'a connection to said turbine wheel,- a second gear ellrlent'y arranged inmeshing relationship to 'the other of said pinions and having a connection to said reaction wheel, said gear elements being in a ratio such that the reaction wheel is driven forward by the turbine wheel at a lesser speed than the latter, an output shaft drivably connected to said planet carrier, and means for taking the reaction of said planetary gear train and said torque converter.

4. A transmission comprising a hydro-kinetic torque converter having rotatable bladed impeller, turbine, and reaction wheels, when rotated, said impeller wheel circulates fluid which acts on said turbine and reaction wheels tending to rotate the turbine wheel forward and the reaction Wheel backward with respect to the impeller wheel, a planetary gear train including a planet carrier supporting a double planet pinion, a gear element arranged in meshing relationship with one of said pinions and having a e being in a ratio such that the reaction wheel is f.

driven forward by the turbine wheel at a lesser speed than the latter, an output shaft drivably connected to said planet carrier, and a third gear element arranged in meshing relationship with said one pinion, and means for holding said third gear element against rotation during torque multiplication.

5. A transmission comprising a hydraulic torque converter having rotatable bladed impeller, turbine, and reaction wheels, said transmission having a stage of operation wherein rotation of said impeller wheel circulates uid which acts on said turbine wheel to drive the same forward at a speed greater than that of the impeller wheel and acts on said reaction wheel tending to drive it in the same direction as the impeller wheel, a rst gear element connected to said turbine wheel, a second gear element connected to saidreaction wheel, a double planet pinion, one of said pinions meshing with the first gear element and the other meshing with the second gear element, an output shaft, a planet carrier supporting said pinions and carried by said output shaft, and means for taking reaction.

6. A transmission comprising a torque converter equipped with impeller, turbine, and reaction wheels when rotated, said impeller wheel circulates iiuid which acts on said turbine and reaction wheels tending to drive the former forward and the latter backward with respect to said impeller wheel, a first gear connected to said turbine wheel, a second gear connected to said reaction wheel, a double planet pinion having different pitch diameters, the smaller pinion meshing with said second gear ,and the larger pinion meshing with said first gear so that rotation of said turbine wheel drives said reaction wheel forward at a lesser speed than the turbine wheel, output means including a planet car- 10'- rier for supporting said' pinion, and means for taking reaction;

7. A transmission comprising a hydraulic torque converter having rotatable bladed impeller, turbine', and reaction wheels, said transmission having a rst stage fof operation wherein-'rotation of said impeller wheel causes -fiui'd to act on said` turbine wheel to drv'ethe same fiorward at a lesservspeed 'than that of thei'mpeller wheel, and on said ureaction' wheel tending to drive itbac'kward, a first geareleinent connected to said turbine wheel, a second gear element connected to said reaction wheel, a third gear element, means for holding said third gear element, a double planet pinion interposed between said gear elements to provide a positive forward drive for said reaction wheel during the rst stage of operation, a planet carrier supporting said double planet pinion, and an output shaft to which the planet carrier is connected for driving the former, said transmission having a second stage of operation wherein rotation of said impeller wheel causes fluid to act on said turbine wheel to drive it forward at a greater speed than impeller wheel speed, and at the same time the fluid acts on said reaction wheel causing it to rotate forward, whereby the output shaft overdrives the impeller wheel.

8. A transmission including a hydraulic torque converter having rotatable bladed impeller, turbine, and reaction wheels, al1 of which rotate forward, a planetary gear train including a planet carrier supporting a double planet pinion, a gear element meshing with one of said pinions and having a connection to said turbine wheel, a second gear element meshing with the other of said pinions and having a connection to said reaction wheel, an output shaft drivably connected to said planet carrier, said reaction and turbine wheels being interconnected through said planetary gear train in such a manner that the latter wheel drives the former wheel forward at a xed ratio during torque multiplication in the converter, after torque multiplication said reaction wheel is rotated forward under the influence of fluid from the impeller wheel, thus producing a forward torque, said planetary gear train capable of combining said forward torque from the reaction wheel with turbine wheel torque, and means connected to said double planet pinion for taking reaction.

9. A transmission including a hydraulic torque converter having rotatable bladed impeller, turbine, and reaction wheels all of which rotate forward, an output shaft, a planet carrier drivably connected to said output shaft and supporting a double planet pinion, means including gears connecting said double planet pinion to the reaction and turbine wheels, said double planet pinion being of different pitch diameters and so related to said gears that at times forward torque from the turbine wheel is transferred to said planet carrier to rotate the output shaft and to drive the reaction wheel forward at a fixed ratio, the ratios RICHARD T. BURNETT.

(References on following page) 1 1 REFERENCES CITED The following references are of record in the Number 12 Name Date Tipton Apr. 14, 1942 Breer et a1. May 26, 1942 Tipton July 28, 1942' Tipton Dec. 29, 1942 MacFarland July 20, 1943 Dufeld Aug. 17, 1943 Swennes Mar. 13, 1945 Dufeld Apr. 10, 1945 Kelbel Aug. 20, 1946 Bauman June 14, 1949 

